US5421306A - Check valve for engine fuel delivery systems - Google Patents

Check valve for engine fuel delivery systems Download PDF

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Publication number
US5421306A
US5421306A US08/206,170 US20617094A US5421306A US 5421306 A US5421306 A US 5421306A US 20617094 A US20617094 A US 20617094A US 5421306 A US5421306 A US 5421306A
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US
United States
Prior art keywords
valve
passage
valve element
fuel
seat
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US08/206,170
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English (en)
Inventor
Edward J. Talaski
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
TI Group Automotive Systems LLC
Walbro Corp
Original Assignee
Walbro Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by Walbro Corp filed Critical Walbro Corp
Priority to US08/206,170 priority Critical patent/US5421306A/en
Assigned to WALBRO CORPORATION reassignment WALBRO CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: TALASKI, EDWARD J.
Priority to JP7036536A priority patent/JP2634383B2/ja
Priority to DE19507321A priority patent/DE19507321C2/de
Priority to FR9502581A priority patent/FR2716936A1/fr
Application granted granted Critical
Publication of US5421306A publication Critical patent/US5421306A/en
Assigned to NATIONSBANK, N.A. reassignment NATIONSBANK, N.A. SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: WALBRO CORPORATION
Assigned to TI GROUP AUTOMOTIVE SYSTEMS, L.L.C. OF DELAWARE reassignment TI GROUP AUTOMOTIVE SYSTEMS, L.L.C. OF DELAWARE ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: WALBRO CORPORATION OF DELAWARE
Assigned to WALBRO CORPORATION reassignment WALBRO CORPORATION RELEASE OF PATENT ASSIGNMENT Assignors: BANK OF AMERICA, N.A. (F/K/A NATIONSBANK, N.A.)
Assigned to JPMORGAN CHASE BANK, N.A. reassignment JPMORGAN CHASE BANK, N.A. SECURITY AGREEMENT Assignors: HANIL USA, L.L.C., TI AUTOMOTIVE, L.L.C., TI GROUP AUTOMOTIVE SYSTEMS, L.L.C.
Assigned to WILMINGTON TRUST (LONDON) LIMITED reassignment WILMINGTON TRUST (LONDON) LIMITED ASSIGNMENT OF SECURITY INTEREST Assignors: JP MORGAN CHASE BANK, N.A.
Assigned to CITIBANK N.A. reassignment CITIBANK N.A. ABL PATENT SECURITY AGREEMENT Assignors: TI GROUP AUTOMOTIVE SYSTEMS, L.L.C.
Assigned to CITIBANK N.A. reassignment CITIBANK N.A. TERM PATENT SECURITY AGREEMENT Assignors: TI GROUP AUTOMOTIVE SYSTEMS, L.L.C.
Assigned to TI AUTOMOTIVE, L.L.C., HANIL USA, L.L.C., TI GROUP AUTOMOTIVE SYSTEMS, L.L.C. reassignment TI AUTOMOTIVE, L.L.C. RELEASE AND TERMINATION OF PATENT SECURITY INTEREST Assignors: WILMINGTON TRUST (LONDON) LIMITED (AS SUCCESSOR IN INTEREST TO JP MORGAN CHASE BANK, N.A.)
Assigned to TI GROUP AUTOMOTIVE SYSTEMS, L.L.C. reassignment TI GROUP AUTOMOTIVE SYSTEMS, L.L.C. RELEASE BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: CITIBANK, N.A.
Assigned to JPMORGAN CHASE BANK, N.A. reassignment JPMORGAN CHASE BANK, N.A. SECURITY AGREEMENT Assignors: HANIL USA, L.L.C., TI AUTOMOTIVE CANADA, INC., TI AUTOMOTIVE LIMITED, TI AUTOMOTIVE, L.L.C., TI GROUP AUTOMOTIVE SYSTEMS S DE R.L. DE C.V., TI GROUP AUTOMOTIVE SYSTEMS, L.L.C.
Anticipated expiration legal-status Critical
Assigned to TI AUTOMOTIVE LIMITED, TI AUTOMOTIVE CANADA, INC., HANIL USA L.L.C., TI AUTOMOTIVE, L.L.C., TI GROUP AUTOMOTIVE SYSTEMS, L.L.C., TI GROUP AUTOMOTIVE SYSTEMS S DE R.L. DE C.V. reassignment TI AUTOMOTIVE LIMITED TERMINATION AND RELEASE Assignors: JPMORGAN CHASE BANK, N.A., AS ADMINISTRATIVE AGENT
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
    • F02M37/0023—Valves in the fuel supply and return system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/06—Check valves with guided rigid valve members with guided stems
    • F16K15/063—Check valves with guided rigid valve members with guided stems the valve being loaded by a spring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves
    • F16K27/0209—Check valves or pivoted valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7904—Reciprocating valves
    • Y10T137/7922—Spring biased
    • Y10T137/7929—Spring coaxial with valve
    • Y10T137/7932—Valve stem extends through fixed spring abutment

Definitions

  • the present invention is directed to fuel delivery systems for internal combustion engines, and more particularly to an improved check valve for disposition between the fuel pump and the engine.
  • Fuel delivery systems of the subject character typically include a pump for delivering fuel under pressure from a supply to a fuel consumer, such as an internal combustion engine. Excess fuel at the engine is returned to the supply tank through a pressure regulator.
  • a check valve is connected between the pump and the engine for preventing back-flow of fuel from the engine to the pump when the pump is turned off. Fuel pressure is thereby maintained at the engine, resulting in reduced start-up time.
  • the check valve includes a valve element biased by a spring against a seat within a fuel passage. That portion of the passage extending from the seat surrounding the valve element is of uniform cylindrical contour so that, after lift of the valve element from the seat, cross sectional area to fluid flow between the valve element and the surrounding wall remains substantially constant and independent of valve lift.
  • U.S. Pat. No. 4,697,995 discloses a check valve of the described construction carried by the housing of a fuel pump, and thus constructed as a unitary assembly with the pump.
  • a general object of the present invention is to provide a check valve that finds particular utility in fuel delivery systems of the subject character, but also enjoys wide application in other flow control environments of similar nature, and that helps reduce or eliminate pressure and flow pulses in the fuel delivery line.
  • Another and more specific object of the invention is to provide a check valve of the described character that exhibits a cross sectional area to fluid flow that increases continuously or substantially continuously, preferably substantially linearly, with fluid pressure and corresponding motion of the valve element against the force of the return spring.
  • a check valve in accordance with a presently preferred embodiment of the invention comprises a valve element, a fluid flow passage surrounding the valve element and having an internal valve seat opposed to the valve element, and a spring positioned within the passage for urging the valve element against the seat.
  • the fluid passage internal wall surface extending downstream from the valve seat is contoured to cooperate with the valve element such that cross sectional area to fluid flow through the passage surrounding the valve element increases substantially continuously with motion of the valve element within the passage for substantially the entire range of motion of the element within the passage.
  • the fluid passage wall surface downstream of the valve seat lies on a continuous surface of revolution that surrounds the central axis of the passage. Diameter of the fluid passage wall surface portion that surrounds the valve element increases substantially monotonically from the valve seat for an axial distance that substantially corresponds to maximum travel of the valve element against the spring.
  • the check valve is positioned between the pump and the engine for preventing back-flow of fuel from the engine to the pump. Excess fuel at the engine is returned to the supply through a pressure regulator, which also controls pump operating pressure.
  • the valve has a flow passage with a central axis and a valve seat orientated away from the pump.
  • the valve element is positioned within the passage for axial motion against a coil spring as a function of fuel flow from the pump.
  • a first small portion of the passage surrounding the valve element immediately adjacent to the valve seat is substantially cylindrical.
  • a second portion of the wall surface that surrounds the valve element for a major portion of its travel has a cross section to fluid flow that increases substantially monotonically, preferably conically, from the seat for an axial distance that at least corresponds to travel of the valve element against the spring within the limited flow range required at the valve.
  • a substantially cylindrical third portion of the valve passage is positioned adjacent to the second portion and surrounds the valve element, and the valve element is slidably disposed in a keeper in this cylindrical third portion of the passage.
  • the valve element in the preferred embodiments of the invention has a conical valve head so that, at any position of the valve element within the passage, the cross section area to fluid flow--i.e., the radial separation between the valve head and the surrounding passage surface--decreases uniformly in the direction of fluid flow.
  • This construction makes the valve element essentially self-centering during operation.
  • axial and lateral motions of the valve element are stabilized in the preferred implementation of the invention, greatly reducing pressure pulses delivered from the pump to the engine.
  • the valve element may be of plastic or brass construction or may be of stainless steel construction in alternate fuel applications.
  • the valve head comprises a hollow rubber cone insert molded or snapped onto the valve element.
  • FIG. 1 is a partially schematic and partially sectional view in side elevation of a fuel delivery system that includes a check valve in accordance with one presently preferred embodiment of the invention
  • FIG. 2 is a sectional view taken substantially along the line 2--2 in FIG. 1;
  • FIGS. 3-5 are fragmentary sectional views on an enlarged scale that illustrate operation of the check valve in FIG. 1;
  • FIG. 6 is a graph useful in discussing operation of the check valve in accordance with the invention.
  • FIG. 7 is a partially sectioned elevational view of a valve element in accordance with a modified embodiment of the invention.
  • FIGS. 8 and 9 are fragmentary views taken substantially along the lines 8--8 and 9--9 in FIGS. 7 and 8 respectively.
  • FIG. 1 illustrates a fuel delivery system 20 in accordance with one presently preferred embodiment of the invention as comprising a fuel pump 22 for delivering fuel under pressure from a supply or tank 24 to a fuel rail 25 coupled to a fuel consumer 26, such as an internal combustion engine.
  • a check valve 28 is connected in the fuel line between pump 22 and rail 25 for permitting free flow of fuel from the pump to the fuel rail, but preventing back-flow of fuel from the rail to the pump when the pump is shut off. Excess fuel at rail 25 is returned to tank 24 by a pressure regulator 27.
  • valve 28 includes a sleeve or fitting 30 having an internal passage 32 formed with a valve seat 34.
  • a valve element 36 is positioned within passage 32 downstream of seat 34 with respect to the direction of fuel flow from pump 22 to engine 26.
  • a coil spring 38 is captured in compression between valve element 36 and a keeper 40 within passage 32 for urging valve element 36 against valve seat 34.
  • Flow of fuel from pump 22 urges valve element 36 to the right in FIG. 1 against the force of spring 38, and thereby lifts the valve element from the valve seat to permit passage of fuel therepast.
  • Keeper 40 includes a central sleeve 42 with radially extending ribs 44 that engage passage 32 downstream of seat 34.
  • the enlarged end 46 of keeper 40 is press fitted into a counterbore 48 at the seat-remote end of fitting 30.
  • Valve element 36 has an elongated stem 50 that extends through the internal passage 52 of keeper 40, being retained therein by the enlargement 54 at the end of stem 50.
  • Coil spring 38 surrounds stem 50 and is captured between the head 56 of valve element 36 and the internal shoulder 58 of keeper 40.
  • a resilient conical cap 60 of rubber or other suitable construction has an inward lip 62 that is received in an annular groove on head 56 to retain cap 60 on head 56.
  • Passage 32 includes a conical portion 66 that forms seat 34.
  • a small substantially cylindrical portion 68 surrounds head 56 and is contiguous with portion 66.
  • a conical surface 70 opens downstream of surface portion 68 coaxially with valve element 36.
  • the axial face 71 of keeper 40 forms an axial stop for valve head 56 to limit motion thereof against spring 58.
  • Axial dimension of surface portion 70 is coordinated with travel of valve element 36 within fitting 30 so that cross sectional area to fluid flow within passage 32 around valve element 36 increases continuously substantially throughout travel of element 36 within fitting 30.
  • FIG. 3 is a fragmentary view on an enlarged scale of a portion of valve 28 in FIG. 1 showing valve element 36 seated by spring 38 against valve seat 34.
  • valve element 36 As flow of fuel from pump 22 (FIG. 1) increases, valve element 36 is initially lifted from seat 34 against the spring force to provide a minimum annular area 72 (FIG. 4) for fluid flow between valve element 36 and surface portion 68.
  • the conical contour of surface portion 70 provides an increasing separation between the surface and the opposing edge of valve element 36, and thus a continuously increasing annular area for fluid flow between the valve element and the surrounding surface.
  • Such fluid flow area continues to increase with valve element motion or lift at least substantially to the limit of travel of the valve element, at which point (FIG. 5) maximum separation 74 provides maximum annular area for fluid flow between the valve element and the surrounding passage wall surface.
  • FIG. 6 illustrates the lift v. flow characteristics for the valve 28 of FIGS. 1-5.
  • valve 28 is designed to yield a substantially linear flow characteristic over a design operating range between a minimum lift (FIG. 4) and a maximum lift (FIG. 5).
  • Overall design flow range accommodates variability of pump 22 (FIG. 1), pressure regulator 27, fuel temperature and pumps drive voltage.
  • lift would be expected to fluctuate between the points 76,78 as a function of engine demand, corresponding to a normal flow area range 80.
  • Minimum expected lift 82 may occur under low voltage or hot fuel conditions, while maximum expected lift 84 may occur at high voltage or cold fuel conditions, for example.
  • valve 28 does not fluctuate between open and closed positions within the design operation range. This helps present extremes of flow and pressure pulsations.
  • the operating conditions of FIGS. 4 and 5 thus correspond to minimum and maximum fluid flow conditions, and dimensions of valve 28 are selected in correspondence with actual fluid flow requirements at these stages.
  • conical cap 60 cooperates with the outer edge of valve element flange 63 to form a substantially conical valve element surface opposed to fuel flow. That is, the outer diameter of flange 63 is contoured essentially to continue the conical surface of cap 60. Preferably the conical outer diameter of flange 63 is at a slightly lesser angle to the axis than the outer surface of cap 60. It will thus be seen in FIG. 5 that the cross sectional area to fluid flow--i.e., the radial spacing between surface 70 and cap 56/flange 63 decreases uniformly in the direction of fluid flow for any given position of the valve element to a minimum area at the plane of flange 63. This construction makes valve element 36 essentially self-centering within passage 32, essentially eliminating valve noise due to radial motion and vibration at the valve head.
  • FIGS. 7-9 illustrate a modified valve element 90, in which the body 92 is of plastic composition and cap 94 is insert molded onto body 92 adjacent to flange 93.
  • Body 92 has flats 96 on the opposed sides of stem 98, and an enlargement 100 is formed by a rib for retaining the valve element in keeper 40 (FIGS. 1-2).
  • Flats 96 help reduce the likelihood of valve malfunction due to flash from the molding process.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Check Valves (AREA)
  • Fuel-Injection Apparatus (AREA)
US08/206,170 1994-03-07 1994-03-07 Check valve for engine fuel delivery systems Expired - Lifetime US5421306A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US08/206,170 US5421306A (en) 1994-03-07 1994-03-07 Check valve for engine fuel delivery systems
JP7036536A JP2634383B2 (ja) 1994-03-07 1995-02-24 エンジン燃料送出装置用逆止弁
DE19507321A DE19507321C2 (de) 1994-03-07 1995-03-02 Kraftstoff-Zuführeinrichtung für eine Brennkraftmaschine
FR9502581A FR2716936A1 (fr) 1994-03-07 1995-03-06 Circuit de distribution de carburant pour moteur à combustion interne.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US08/206,170 US5421306A (en) 1994-03-07 1994-03-07 Check valve for engine fuel delivery systems

Publications (1)

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US5421306A true US5421306A (en) 1995-06-06

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JP (1) JP2634383B2 (it)
DE (1) DE19507321C2 (it)
FR (1) FR2716936A1 (it)

Cited By (38)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5546912A (en) * 1993-12-14 1996-08-20 Yamaha Hatsudoki Kabushiki Kaisha Fuel supply device
US5603302A (en) * 1994-08-25 1997-02-18 Nippondenso Co., Ltd. Fuel supply system for internal combustion engine
US5715797A (en) * 1995-06-28 1998-02-10 Nippondenso Co., Ltd. Fuel supply system for internal combustion engine and method of adjusting it
US5749345A (en) * 1995-11-02 1998-05-12 Bayerische Motoren Werke Aktiengesellschaft Fuel system
US5752481A (en) * 1993-10-18 1998-05-19 Valve Maintenance Corporation Injection valve assembly for an internal combustion engine
US6067963A (en) * 1995-10-09 2000-05-30 Nippondenso Co., Ltd. Fuel supply system with fuel evaporation prevention
US6186420B1 (en) * 1998-07-22 2001-02-13 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
US6223731B1 (en) 1996-09-09 2001-05-01 Denso Corporation Fuel feeding apparatus with response delay compensation
US6269828B1 (en) 1999-12-06 2001-08-07 Siemens Automotive Corporation Pressure regulator valve seat with mutually orthogonal flow channels
US6286486B1 (en) * 1999-12-06 2001-09-11 Siemens Automotive Corporation Fuel system including a pressure regulator
US6334460B1 (en) 1999-12-06 2002-01-01 Siemens Automotive Corporation Pressure regulator baffle seat with radial flow paths
US6401693B1 (en) * 2000-09-01 2002-06-11 Schrader-Bridgeport International, Inc. Pressure spike attenuator for automotive fuel injection system
US6481418B1 (en) * 2000-10-23 2002-11-19 Delphi Technologies, Inc. Fuel pressure regulator
US6648016B2 (en) 2002-01-24 2003-11-18 Alfmeier Corporation Valve assembly for a fuel tank
US20040007271A1 (en) * 2002-06-01 2004-01-15 Michael Kuehn Check valve
US20040069353A1 (en) * 2002-10-09 2004-04-15 Pickelman Dale M. Check valve for fuel pump
US20040069352A1 (en) * 2002-06-04 2004-04-15 Thomas Wieland Check valve
US6748964B2 (en) * 2001-08-03 2004-06-15 Siemens Automotive Corporation Flow-through pressure regulator self-contained valve assembly
US6758235B2 (en) 2002-09-30 2004-07-06 Alfmeier Prazision Ag Baugruppen Und Systemlosungen Vapor control valve with a metallic sealing element
US20040173265A1 (en) * 2003-03-04 2004-09-09 Roth Robert A. Check valve for fuel pump
US20050016599A1 (en) * 2003-07-22 2005-01-27 Talaski Edward J. Pressure control valve
US6877525B2 (en) 2001-11-07 2005-04-12 Delphi Technologies, Inc. Check valve for fuel pump
EP1528304A1 (en) * 2003-10-31 2005-05-04 Eaton Corporation Valve assembly and method
US20060220446A1 (en) * 2005-03-30 2006-10-05 Jensen Daniel W Check valve for high-pressure fluid reservoir
US20060243329A1 (en) * 2005-04-29 2006-11-02 Ti Group Automotive Systems, L.L.C. Check valve apparatus for fuel delivery systems
US20060272711A1 (en) * 2003-07-22 2006-12-07 Ti Group Automotive Systems, L.L.C. Pressure control valve
WO2007076375A2 (en) 2005-12-20 2007-07-05 Ds Smith Plastics Limited Valve for a fluid flow connector having an overmolded plunger
CN100348435C (zh) * 2003-07-25 2007-11-14 现代自动车株式会社 Lpi车辆用无回流燃料系统
US20080047621A1 (en) * 2004-08-13 2008-02-28 Ralph Ittlinger Check Valve
WO2013117200A1 (en) * 2012-02-07 2013-08-15 Volvo Lastvagnar Ab Fuel injection system
EP2644954A1 (en) * 2012-03-30 2013-10-02 TI Group Automotive Systems, L.L.C. Fuel system valve assembly
ITBS20120113A1 (it) * 2012-07-23 2014-01-24 Iricom S R L Cartuccia autoportante per una valvola di non ritorno
US8939736B2 (en) 2011-11-30 2015-01-27 Walbro Engine Management, L.L.C. Fuel pump assembly
US20190040965A1 (en) * 2017-01-31 2019-02-07 Fujikin Incorporated Flow dividing valve
CN110529636A (zh) * 2019-09-17 2019-12-03 苏州沃达园林机械有限公司 一种快接式单向阀
CN113454327A (zh) * 2019-02-20 2021-09-28 皮尔伯格有限责任公司 用于燃料截止阀的限流装置
US11156193B2 (en) 2018-03-20 2021-10-26 Walbro Llc Fuel pump assembly with diverted flow
US11846259B2 (en) * 2021-11-22 2023-12-19 Coavis Pressure regulator and fuel pump module having the same

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DE102009046119A1 (de) 2009-10-28 2011-05-12 Robert Bosch Gmbh Ventil

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US4537384A (en) * 1984-07-17 1985-08-27 Brunswick Corporation In-line check valve having combined downstream poppet support and flow control elements
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US5148792A (en) * 1992-01-03 1992-09-22 Walbro Corporation Pressure-responsive fuel delivery system
US5196493A (en) * 1990-05-02 1993-03-23 Ciba-Geigy Corporation Polymers and hard, gas-permeable contact lenses made therefrom
US5289810A (en) * 1992-07-29 1994-03-01 Robert Bosch Gmbh Arrangement for supplying fuel from supply tank to internal combustion engine of motor vehicle

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US3756273A (en) * 1971-11-22 1973-09-04 R Hengesbach Valve
DE2415298A1 (de) * 1974-03-29 1975-10-23 Bosch Gmbh Robert Rueckschlagventil fuer niederdruckeinspritzanlagen
US3945396A (en) * 1975-02-24 1976-03-23 Hengesbach Robert W Rapid seating check valve
GB1528120A (en) * 1975-10-21 1978-10-11 Thorogood A Non-drip flow valve
US4271862A (en) * 1978-05-08 1981-06-09 Inter Ocean N.V. Check valve and method of manufacturing said check valve
US4697995A (en) * 1982-07-29 1987-10-06 Walbro Corporation Rotary positive displacement fuel pump with purge port
US4539959A (en) * 1984-02-27 1985-09-10 General Motors Corporation Fuel injection system with fuel flow limiting valve assembly
US4537384A (en) * 1984-07-17 1985-08-27 Brunswick Corporation In-line check valve having combined downstream poppet support and flow control elements
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US5196493A (en) * 1990-05-02 1993-03-23 Ciba-Geigy Corporation Polymers and hard, gas-permeable contact lenses made therefrom
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Cited By (63)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5752481A (en) * 1993-10-18 1998-05-19 Valve Maintenance Corporation Injection valve assembly for an internal combustion engine
US5546912A (en) * 1993-12-14 1996-08-20 Yamaha Hatsudoki Kabushiki Kaisha Fuel supply device
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Also Published As

Publication number Publication date
FR2716936A1 (fr) 1995-09-08
DE19507321C2 (de) 2001-03-08
JPH07293386A (ja) 1995-11-07
DE19507321A1 (de) 1995-09-14
JP2634383B2 (ja) 1997-07-23
FR2716936B1 (it) 1997-02-14

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